CN110100118A - Torque coupling arrangement and its manufacturing method with torque-vibration damper and unidirectional turbine clutch - Google Patents

Torque coupling arrangement and its manufacturing method with torque-vibration damper and unidirectional turbine clutch Download PDF

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Publication number
CN110100118A
CN110100118A CN201780078988.5A CN201780078988A CN110100118A CN 110100118 A CN110100118 A CN 110100118A CN 201780078988 A CN201780078988 A CN 201780078988A CN 110100118 A CN110100118 A CN 110100118A
Authority
CN
China
Prior art keywords
turbine
clutch
unidirectional
torque
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201780078988.5A
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Chinese (zh)
Inventor
S.耶雅巴兰
A.德普拉特
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Farokepeco Inc
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Farokepeco Inc
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Filing date
Publication date
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Publication of CN110100118A publication Critical patent/CN110100118A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/40—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which the or each axially-movable member is pressed exclusively against an axially-located member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D47/00—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings
    • F16D47/04—Systems of clutches, or clutches and couplings, comprising devices of types grouped under at least two of the preceding guide headings of which at least one is a freewheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H41/28—Details with respect to manufacture, e.g. blade attachment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/246—Details relating to one way clutch of the stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0289—Details of friction surfaces of the lock-up clutch
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Abstract

A kind of dynaflow torque converter, comprising: shell, impeller and turbine, unidirectional turbine clutch and torque-vibration damper with locking surface.The unidirectional turbine clutch includes the outer ring for being non-rotatably connected to turbine case, inner ring and joint element, and joint element allows outer ring only in a circumferential direction relative to inner ring rotary motion.Turbine is nonrotatably coupling to the outer ring of unidirectional turbine clutch.Torque-vibration damper includes input link, multiple elastic components circumferentially acted on and the output link that input link is elastically attached to by elastic component.The output link of torque-vibration damper is non-rotatably attached to turbine.

Description

Torque coupling arrangement with torque-vibration damper and unidirectional turbine clutch and its Manufacturing method
Technical field
The present disclosure relates generally to fluid coupling, relate more specifically to the mixed of the one-way clutch for turbine Close the torque-converters and its manufacturing method of power car.
Background technique
Currently, due to needing to reduce fuel consumption and limitation pollution, the demand to " cleaning " vehicle tends to increase.In general, In order to realize the demand, hybrid power system is being developed.Hybrid vehicle is for example known to have torque-converters and regeneration system Dynamic, wherein alternating current generator (or generator) during vehicle braking for collecting kinetic energy.Alternating current generator will be collected dynamic It can be converted into electric energy, to be, for example, the energy storage device charging in the form of one group of supercapacitor or battery.Then will This energy being recovered returns in various Electrical and Electronic equipment included by motor vehicles.Electric energy can also be used for starting heat Force engine, or the torque of auxiliary Thermal Motor.
In some operating conditions of hybrid vehicle, such as in sliding mode, engine braking modes and regeneration mould In formula, the output hub for torque-converters can quickly be rotated than the turbine of torque-converters.In general, output hub and turbine are non-rotating Ground connection.Therefore, it is sliding, in engine braking or regeneration mode, the typical fluid in the rotation reversion converter of turbine Flow pattern, and fluid " pumping " is arrived impeller by turbine.This operation of turbine is undesirable, because the rotation of turbine adds Oil in hot torque-converters leads to excessive heat loss, and even damages torque-converters in some cases.
In addition, sliding period in hybrid vehicle, the resistance as caused by the turbine of torque-converters reduces hybrid power The efficiency of the electric notor of vehicle, because the resistance generates reactive torque and reduces the effective torque of electric notor.
Moreover, in some operating conditions, such as the regeneration mode in hybrid vehicle, it is expected that preventing internal combustion engine Rotation.In addition, some torques can be transmitted to impeller by the rotation of turbine, it is then passed to internal combustion engine.Known use Mechanical device, such as one-way clutch or gear mechanism disconnect input shaft from torque associated with regeneration mode.
Summary of the invention
Technical problem
Although traditional fluid dynamics torque coupling arrangement (including but not limited to discussed above) has been demonstrated Can be used for hybrid vehicle, but allow the turbine for the torque-converters being used together with hybrid vehicle during regeneration mode from The improvement for the one-way clutch that transmission input shaft disconnects be it is feasible, its performance and cost can be enhanced in this.
Solution to the problem
According to the first aspect of the invention, a kind of fluid for drive shaft and driven shaft to be linked together is provided to move Power torque-converters.Torque-converters includes that can rotate and have the shell of locking surface around rotation axis, can be rotated around rotation axis Impeller, the turbine that can be rotated around rotation axis and axially be oppositely disposed with impeller are axial to determine between impeller and turbine Son, the unidirectional turbine clutch and torque-vibration damper for allowing turbine to be only rotated in a circumferential direction. Turbine is coaxially aligned with impeller and can be hydrodynamically rotatably driven by impeller.Unidirectional turbine clutch includes: can not It is rotationally connected to the outer ring of turbine；The inner ring being radially arranged in outer ring, and be positioned radially between outer ring and inner ring Multiple joint elements, the multiple joint element be configured as allow outer ring it is only enterprising in a circumferential direction relative to inner ring Row rotary motion.Turbine is nonrotatably coupling to the outer ring of unidirectional turbine clutch.Turbine includes turbine shroud and at least one A holding plate, the holding plate are integrally extended radially inwardly from turbine shroud with turbine shroud.At least one described holding plate is set It sets between stator and turbine one-way clutch.Torque-vibration damper includes can be more around the input link that rotation axis rotates A elastic component circumferentially acted on, and it is elastically attached to by elastic component the output link of input link.Twisting vibration The output link of damper is non-rotatably attached to turbine.
According to the second aspect of the invention, it provides a kind of for assembling for drive shaft and driven shaft to be linked together Fluid dynamic torque converter method.It can be around the shell of rotation axis rotation method includes the following steps: providing First shell shell and second shell shell；Pre-assembled torque-converters is provided, the pre-assembled torque-converters includes impeller and leaf Wheel shaft is to the turbine and stator being oppositely disposed；With the unidirectional turbine clutch of offer, the unidirectional turbine clutch allows turbine Only it is rotated in a circumferential direction.Turbine includes turbine shroud and at least one holding plate, the holding plate and whirlpool Wheel shell is integrally extended radially inwardly from turbine shroud.Unidirectional turbine clutch includes: outer ring；It is radially arranged in outer ring Inner ring；And the multiple joint elements being radially positioned between outer ring and inner ring, the multiple joint element are configured to permit outer Ring is only rotated in a circumferential direction relative to inner ring.This method is further comprising the steps of: by turbine and rotation It is non-rotatably connected to axis coaxle the outer ring of unidirectional turbine clutch, so that at least one holding plate setting of turbine exists Between stator and turbine one-way clutch, torque-vibration damper includes can be around the input link, multiple of rotation axis rotation The elastic component that circumferentially acts on and the output link that input link is elastically attached to by elastic component, twisting vibration is damped The output link of device is non-rotatably attached to turbine, and the input link of torsional oscillation fluctuation dampers is passed through to the elasticity circumferentially acted on Component and the output link for being elastically mounted to torque-vibration damper.
It is of the invention including constituting by reading described in detail below, the other aspects of the present invention of exemplary embodiment Partial device, equipment, system, converter, process etc. will become apparent.
Detailed description of the invention
Attached drawing is incorporated to and forms part of this specification.Attached drawing is described and is given below together with generality is given above Exemplary embodiment and method detailed description principle for explaining the present invention.Objects and advantages of the present invention will pass through root The research of following description is become apparent according to attached drawing, identical element is endowed same or similar attached in the accompanying drawings Icon note, and in the accompanying drawings:
Fig. 1 is that the part half according to the present invention in the axial cross section of the dynaflow torque converter of the first exemplary embodiment regards Figure；
Fig. 2 is the turbine of the dynaflow torque converter of the first exemplary embodiment, unidirectional turbine clutch according to the present invention With half view of part in the axial cross section of lock piston；
Fig. 3 is the turbine of the dynaflow torque converter of the first exemplary embodiment and unidirectional turbine clutch according to the present invention Axial cross section in part half view；
Fig. 4 is half view of section of the unidirectional turbine clutch of Fig. 3；
Fig. 5 is the outer of the unidirectional turbine clutch of the dynaflow torque converter of the first exemplary embodiment according to the present invention The front plan view of ring；
Fig. 6 is the outer ring of the unidirectional turbine clutch of the dynaflow torque converter of the first exemplary embodiment according to the present invention Perspective view；
Fig. 7 A is the partial perspective forward sight of the turbine of the dynaflow torque converter of the first exemplary embodiment according to the present invention Figure；
Fig. 7 B is the perspective view of the substitution turbine of the dynaflow torque converter of the first exemplary embodiment according to the present invention；
Fig. 8 is the unidirectional turbine clutch with the dynaflow torque converter of the first exemplary embodiment according to the present invention The perspective view of turbine；
Fig. 9 is the planar rear view of the turbine of the dynaflow torque converter of the first exemplary embodiment according to the present invention, With installation to its unidirectional turbine clutch；
Figure 10 is the part half in the axial cross section of the dynaflow torque converter of the second exemplary embodiment according to the present invention View；
Figure 11 is the turbine of the dynaflow torque converter of the second exemplary embodiment and unidirectional turbine clutch according to the present invention Half view of part in the axial cross section of device；
Figure 12 is half view of section of the unidirectional turbine clutch of Figure 11；
Figure 13 is the part half in the axial cross section of the dynaflow torque converter of third exemplary embodiment according to the present invention View；
Figure 14 is the turbine of the dynaflow torque converter of third exemplary embodiment, unidirectional turbine clutch according to the present invention With half view of part in the axial cross section of lock piston；
Figure 15 is the turbine of the dynaflow torque converter of third exemplary embodiment and unidirectional turbine clutch according to the present invention Half view of part in the axial interface of device；
Figure 16 is half view of section of the unidirectional turbine clutch of Figure 15；
Figure 17 A is the partial perspective forward sight of the turbine of the dynaflow torque converter of third exemplary embodiment according to the present invention Figure；
Figure 17 B is the partial perspective backsight of the turbine of the dynaflow torque converter of third exemplary embodiment according to the present invention Figure；
Figure 18 is the planar rear view of the turbine of the dynaflow torque converter of third exemplary embodiment according to the present invention, It has installation to its unidirectional turbine clutch；
Figure 19 is the part half in the axial cross section of the dynaflow torque converter of the 4th exemplary embodiment according to the present invention View；
Figure 20 is the turbine of the dynaflow torque converter of the 4th exemplary embodiment, unidirectional turbine clutch according to the present invention With half view of part in the axial cross section of lock piston；
Figure 20 is the turbine of the dynaflow torque converter of the 4th exemplary embodiment and unidirectional turbine clutch according to the present invention Half view of part in the axial cross section of device；
Figure 21 is the turbine of the dynaflow torque converter of the 4th exemplary embodiment and unidirectional turbine clutch according to the present invention Half view of part in the axial cross section of device；With
Figure 22 is half view of section of the unidirectional turbine clutch of Figure 21.
Specific embodiment
Now with detailed reference to exemplary embodiment of the present invention shown in the drawings and method, wherein in all attached drawings In, identical appended drawing reference indicates identical or corresponding part.It is to be noted, however, that the present invention is widely square at it The explanation that face is not limited to detail, representative device and method and exemplary embodiment and method is combined to show and describe Property example.
It is considered as that the attached drawing of a part of entire written description is read that this description of exemplary embodiment, which is intended to be combined with, It reads.In the description, such as "horizontal", " vertical ", " upward ", " downward ", "upper", "lower", " right side ", " left side ", " top " and " bottom Portion " and its derivative (for example, " horizontally ", " down ", " upward " etc.) should be interpreted to refer to as described below or such as Orientation shown in the drawings under discussion.These relative terms are for the convenience of description, being usually not intended to require specifically to take To.Term about the attachment of " connection " and " interconnection ", connection etc. refers to such relationship, wherein structure otherwise directly Ground or by the way that intermediate structure is indirectly secured to one another or attachment, and removable or rigidity attachment or association, unless otherwise It clearly states.Term " being operably connected " is such attachment, connection or connection, and dependency structure is allowed to rely on the relationship such as Intention operates like that.In addition, word used in claim "one" and " one " mean " at least one (a) ".
Such as in the accompanying drawings on the whole for the first exemplary embodiment of the dynaflow torque converter of hybrid vehicle Indicated by appended drawing reference 10, picture 1-4 in fragmentary sectional view in best seen from.Fluid dynamics torque-converters 10 can be with Known mode operates, fluidly to couple the drive shaft and driven shaft of motor vehicles (such as automobile).In a typical case, it drives Moving axis is the output shaft of the internal combustion engine (not shown) of motor vehicles, and driven shaft is connected to the fluid drive of motor vehicles Device.
Fluid dynamics torque-converters 10 includes that can be provided entirely in shell around the seal casinghousing 12 of rotation axis X rotation Tprque convertor 14, torque-vibration damper (referred to herein as damper assembly) 16 in 12 and rotary shaft can also be surrounded The friction lock-up clutch 18 of line X rotation.Seal casinghousing 12 is at least partially filled with fluid, such as oil or power transmitting fluids.It turns round Rotational oscillation fluctuation dampers 16 and friction lock-up clutch 18 are also disposed in shell 12.The attached drawing being discussed herein shows half view, That is, part or the section of the fluid dynamics torque-converters 10 above rotation axis X.On the whole, torque-converters 10 is about rotary shaft Line X is symmetrical.Herein, axial orientation and radial oriented is considered relative to the rotation axis X of torque-converters 10.It is such as " axial The relative terms on ground ", " radially " and " circumferentially " are respectively relative to be parallel to rotation axis X, perpendicular to rotation axis X and It is circumferentially orientated around rotation axis X.
It include first shell shell (or cover housing) according to the seal casinghousing 12 of the first exemplary embodiment as shown in Figure 1 201With second shell shell (or impeller housing) 202, first shell shell 201With second shell shell 202Immovably (that is, fixedly) be hermetically interconnected, such as by being welded at weld seam 19 on their outer periphery, but still may be used It is rotated around rotation axis X.First shell shell 12c immovably (that is, fixedly) is interconnected to drive shaft, more typically can not It is movably interconnected to flywheel (not shown), which is fixed to drive shaft so as to non-rotatable relative to drive shaft, so that shell 12 with speed identical with power operation rotation, for transmitting torque.Specifically, in the embodiment shown in fig. 1, shell 12 It is rotatably driven by internal combustion engine, and its flywheel is nonrotatably coupling to by bolt 21.In general, stud 21 is for example It is fastened to the shell 20 by being welded and fixed1.First shell shell 201With second shell shell 202Each of be one (that is, monomer) or single-piece, and can be for example integrally formed by the single piece of metal plate of compression moulding.First shell Shell 201Define locking surface 25, the locking surface 25 is towards the tprque convertor 14 and damper assembly in shell 12 16, as best shown in FIG. 1.
Tprque convertor 14 include impeller (sometimes referred to as pump) 30, turbine 32 and it is axial be plugged on impeller 30 and turbine 32 it Between stator (sometimes referred to as reactor) 34.Impeller 30, turbine 32 and stator 34 are aligned coaxially to each other on rotation axis X.Leaf Anchor ring is collectively formed in wheel 30, turbine 32 and stator 34.As it is known in the art, impeller 30 and turbine 32 can be with fluid (or streams Body power) be connected to each other.
Impeller 30 includes substantially annular, semi-circular (or spill) impeller housing 31, substantially annular bead filler Ring 36 and the impeller blade 37 for fixedly (that is, immovably) being attached to impeller housing 31 and bead filler ring 36, for example, it is logical Cross soldering.The second shell shell 20 of shell 122At least part formed and be used as the impeller housing 31 of impeller assembly 30.Cause This, impeller housing 31 is sometimes referred to as a part of shell 12.As a result, the impeller housing 31 of impeller 30 relative to first shell outside Shell 201It is non-rotatable therefore non-rotatable relative to the drive shaft of engine (or flywheel), and with same with engine output phase Speed rotation.Impeller 30 further includes being fixedly secured to second shell shell 202The impeller boss 22 of (or impeller housing 31).Leaf Wheel hub 22 is arranged to engage with the hydraulic pump of speed changer.Impeller housing 31, bead filler ring 36 and impeller blade 37 usually pass through steel Base is stamped and formed out.
Turbine 32 includes substantially annular turbine shroud 33, substantially annular turbine core ring 38 and multiple turbines Blade 39, the multiple turbo blade 39 fixedly (that is, immovably) are attached to turbine shroud 33 and core ring 38, such as logical Cross soldering.The rotation of impeller 30 is so that power transmitting fluids rotary turbine blade 36 in anchor ring, and therefore revolving wormgear shell 33.Whirlpool Hub cap 33, turbine core ring 30 and turbo blade 31 are usually stamped and formed out by steel billet.
Stator 34 is located between impeller 30 and turbine 32, in an efficient way to reboot fluid from turbine 32 Return to impeller 30.Stator 34 is typically mounted in unidirectional clutch of stator 40, is reversely rotated to prevent fastening 34.First thrust axis Hold 421It is inserted between stator 34 and turbine case 33, and the second thrust bearing 422It is inserted in the impeller of stator 34 and shell 12 Hub 22 or second shell shell 202Between.
As best shown in fig. 1, unidirectional clutch of stator 40 is mounted in the stator hub 35 of stator 34, and including with rotation Shaft axis X coaxial outer ring 44, the inner ring 46 coaxial with rotation axis X, and circumferential setting limit between outer ring 44 and inner ring 46 Multiple voussoirs or cylinder roller 48 in fixed annular space.The inner peripheral surface of inner ring 46 has spline 47, for rotatably It is connected to the periphery of stator axis.
Stator 34 includes annular stator holding plate 50, and unidirectional clutch of stator 40 is maintained in stator hub 35, and is prevented Only the component of unidirectional clutch of stator 40 is moved axially relative to stator hub 35 along the direction of rotation axis X.Stator holding plate 50 With axial inner ends face, the outer ring 44 and inner ring 46 of unidirectional clutch of stator 40 are engaged, so as to by voussoir or cylinder roller 48 It is maintained in stator hub 35.The axially external end face of stator holding plate 50 and the first thrust bearing 421Engagement.According to the first example Property embodiment, stator holding plate 50 are fastened to the stator hub 35 of stator 34.
Lock-up clutch 18 includes substantially annular lock piston 52, which can be along rotation axis X court Locking surface 25 (bonding station (or lockdown mode) of lock-up clutch 18) into the cover housing 12c of shell 12 is axially displaced It is axially moved with the locking surface 25 (disengaged position (or non-locking) of lock-up clutch 18) in the cover housing 12c for leaving shell 12 Position.In other words, lock piston 52 is selectively pressed against the locking surface 25 of shell 12, so that torque-converters 10 be locked between the axles Only, and therefore the sliding motion between turbine 32 and impeller 30 is controlled.
Lock piston 52 includes substantially annular piston main body 54 and annular friction liner 56, and annular friction liner 56 is solid Surely it is attached to piston main body 54, with the locking surface 25 towards shell 12.Piston main body 54, which has, is axially facing shell 12 The engagement surface 55 of locking surface 25.As best shown in fig. 1, annular friction liner 56 passes through known in the art any appropriate Means (such as passing through bonding) are at the outer radial periphery end 54 of piston main body 541Place is fixedly attached to the table of joint of piston main body 54 Face 55.At the radially inner circumference end 54 of piston main body 542Locate axially extending to be substantially cylindrical flange 58, close to rotary shaft Line X is simultaneously coaxial with rotation axis X.
Annular friction liner 56 is made of friction material, to improve frictional behaviour.Alternatively, annular friction liner can be tight It is affixed to the locking surface 25 of shell 12.According to yet another embodiment, the first drag ring or liner are fastened to the locking surface of shell 12 25, and the second drag ring or liner are fastened to the engagement surface 55 of lock piston main body 54.Omit one or two drag ring Within the scope of the invention.In other words, annular friction liner 56 can be fastened to any one of engagement surface, all or It is not fastened to engagement surface.In addition, accoding to exemplary embodiment, the engagement surface 55 of lock piston main body 54 is slightly conical, To improve the engagement of lock-up clutch 18.Specifically, the engagement surface of the annular friction facing 55 of the holding of lock piston main body 54 55 be taper, with the locking surface 25 of shell 12 at 10 ° to 30 ° of angle, to improve the torque capability of lock-up clutch 18. Alternatively, the engagement surface 55 of lock piston main body 54 can be parallel to the locking surface 25 of shell 12.
Dynaflow torque converter 10 further includes unidirectional turbine clutch 60, to prevent turbine 32 from reversely rotating.In other words, Unidirectional turbine clutch 60 allows turbine 32 to be only rotated along a circumferential direction.Unidirectional turbine clutch 60, such as Fig. 4 Best seen in, comprising: the outer ring 62 coaxial with rotation axis X；Inner ring 64, it is coaxial with outer ring 62 and with 62 spaced radial of outer ring It opens, it is mutually rotating to allow outer ring 62 and inner ring 64 to be respectively relative to；With with multiple joint elements 66, the multiple joint portion Part 66 is circumferentially disposed in the annular space limited between outer ring 62 and inner ring 64.Outer ring 62 has annular radial outside track table Face 62R, and inner ring 64 has and radial outside track surface 62RDiametrically and annular radial inner orbit surface spaced apart 64R.As seen best in fig. 4, the radial inner orbit surface 64 of inner ring 64RIt is arranged radially at the radial outside track surface of outer ring 62 62RInside.Joint element 66 is configured to engage outside track surface 62 diametricallyRWith inner orbit surface 64R。
Joint element 66 is configured to that outer ring 62 is selectively made non-rotatably to be joined to inner ring 64 and selectively make Outer ring 62 is rotatably separated with inner ring 64.An exemplary embodiment of the present invention, joint element 66 are to be distributed along circumferential direction Voussoir element.Sprag type one-way turbine clutch 60 further includes for voussoir 66 to be maintained on the peripheral side of annular space Outboard cage 67o, inboard cage 67i and tape spring for being maintained at voussoir 66 on the inner circumferential side of annular, such as schemes Best seen in 2 and 6.Tape spring is ring spring component, is configured to through its elastic force between outer ring 62 and inner ring 64 Radially biased voussoir 66.The radial outer end of voussoir 66 is configured to the radial outside track surface 62 of engagement outer ring 62R, and voussoir 66 Radial inner end is configured to engage the radial inner orbit surface 64 of the inner ring 64 of unidirectional turbine clutch 60R.Alternatively, joint element It can be roller or wedge-shaped element.
In other words, outer ring 62 can only revolve in a circumferential direction relative to the inner ring 64 of unidirectional turbine clutch 60 Turn.The inner peripheral surface of inner ring 64 has spline 65, for being rotationally coupled to the periphery of transmission input shaft.Therefore, unidirectionally The inner ring 64 of turbine clutch 60 defines the output hub of dynaflow torque converter 10.As further shown in Figure 1, piston main body 54 cylindrical lip 58 axially slidably (that is, movably) is installed to output hub 64.Therefore, lock piston 52 can be relative to defeated Hub 64 is rotated and is moved axially along rotation axis X out, correspondingly to enter and exit lockdown mode.It is installed to the diameter of output hub 64 Sealing is formed in the interface of transmission input shaft and output hub 64 to the containment member 78 of inner peripheral surface.In addition, turbine 32 can It is rotated around rotation axis X relative to output hub 64.
Exporting hub 64 has annular piston flange 68, which extends axially outward and limit from output hub 64 Substantially cylindrical piston face 69, for making lock piston 52 center and being sliding engaged the cylindrical lip of lock piston 52 58, as best seen in Fig. 1 and 3.Specifically, the cylindrical lip 58 of lock piston 52 be installed to output hub 64, so as to relative to The cylinder-piston surface 69 of output hub 64 centers, is rotatable and axially slidably shift.Output hub 64 also draws with annular Guide rib 70 extends axially outward from output hub 64 and limits the outside guiding surface 71 of annular (such as cylindricality) diameter, for unidirectional The outer ring 62 of turbine clutch 60 center and radial support, as best shown in figs. 3 and 4.Export the plunger flange of hub 64 68 radially outer piston surface 69 includes the annular groove 92 for receiving containment member, and the containment member is, for example, O-ring 93.
The outer ring 62 of unidirectional turbine clutch 60 includes main body 72, and main body 72 has substantially cylindrical radially-outer surface 73, and (that is, flat) directing plate 74 including the substantially annular and plane that are extended radially inwardly from main body 72.In Fig. 3 Best shown, the diameter for the guiding rib 70 that the radial inner end (or distal end) 75 of directing plate 74 is sliding engaged output hub 64 guides outward Surface 71, to make the outer ring 62 of unidirectional turbine clutch 60 center and radial support outer ring 62.In addition, directing plate 74 configures It is maintained between outer ring 62 and inner ring 64 at by joint element 66, and prevents 66 He of joint element of unidirectional turbine clutch 60 Inner ring 64 is axially moved relative to outer ring 62 along rotation axis X in the left to right direction, as shown in Figure 2.According to Exemplary embodiment of the present invention, the directing plate 74 and outer ring 62 of unidirectional turbine clutch 60 are one (or monomer) component, example Such as be made of single component, as in Fig. 3 best seen from but it is also possible to be the separation unit being fixed together.
Turbine 32 further include: one or more (preferably three) coupling members 77A, from the radial direction of annular turbine shell 33 Inner end 33i is along towards cover housing 201Direction substantially axial outwardly extend；With one or more (preferably three) holding plates 77R, from the radial inner end 33i of annular turbine shell 33 it is approximately radial extend internally by joint element 66 and with unidirectional whirlpool The inner ring 64 of wheel clutch 60 is partly overlapped, as best seen in Fig. 2,5,6 and 7A.Each holding plate 77RWith most interior Free distal end, as best seen in figure 7a.First exemplary embodiment according to the present invention has coupling member 77AAnd holding Plate 77RTurbine case 33 be one (or monomer) component, such as be made of single component, such as be made up of punching press, but can To be the separation unit being permanently connected together.
Alternatively, as best seen in Fig. 7 B, turbine 32 is replaced by turbine 32', and turbine 32' includes: substantially annular Turbine case 33'；One or more (preferably three) coupling members 77A, from annular turbine shell 33' radial inner end 33i along court To cover housing 201Direction substantially axial extend outwardly；And one or more (preferably three) holding plates 77R, from annular turbine The radial inner end 33i of shell 33' is approximately radial extend internally by joint element 66 and in unidirectional turbine clutch 60 Ring 64 is partly overlapped.Holding plate 77RInner terminal monolithically interconnected by annular section 77C, as best seen in Fig. 7 B.Whirlpool The annular section 77C for taking turns 32' is the first thrust bearing 421Supporting contact surface is provided.In other words, the first thrust bearing 421Folder Between the annular section 77C and stator holding plate 50 of turbine 32'.First exemplary embodiment according to the present invention has connection Connection member 77A, holding plate 77RAlternate embodiment with the turbine case 33' of annular section 77C is one (or monomer) component, example Such as, it is made of single component, such as by punching press but it is also possible to be the separation unit being permanently connected together.
As best seen in Fig. 3-6, the outer ring 62 of unidirectional turbine clutch 60 includes at least one, preferably multiple recesses (or recess portion) 63, the coupling member 77 of each recess and turbine 32AIn a complementation.Specifically, recess 63 is formed in unidirectionally In the cylindricality radially-outer surface 73 of the main body 72 of the outer ring 62 of turbine clutch 60, as in Fig. 4-7 best seen from.Turbine 32 is not It is rotationally coupled to the outer ring 62 of unidirectional turbine clutch 60.Specifically, as in Fig. 2,3 and 8 best seen from, each connection Component 77AMatchingly one in (positively) engagement recesses 63, so as not to be rotationally coupled unidirectional turbine clutch 60 outer ring 62 and turbine 32.First exemplary embodiment according to the present invention, outer ring 62 has there are three recess 63, and turbine 32 There are three complementary coupling members 77 for toolA。
In addition, the holding plate 77 of turbine 32RIt is arranged in the first thrust bearing 421Between unidirectional turbine clutch 60, such as scheme In 1 best seen from.Holding plate 77RIt is configured to for joint element 66 being maintained between outer ring 62 and inner ring 64, and prevents list To turbine clutch 60 joint element 66 and inner ring 64 relative to outer ring 62 along rotation axis X on direction from right to left Axial movement, as shown in Figs. 1-3.
In some operating conditions of hybrid vehicle, such as in sliding mode, engine braking modes and regeneration mould In formula, the output hub 64 for torque-converters 10 can quickly be rotated than the turbine 32 of torque-converters 10.Therefore, unidirectional turbine clutch Device 60 prevents the resistance generated by turbine 32 and prevents the reactive torque (effect of its electric notor for usually reducing hybrid vehicle Rate), to avoid the effective torque for the electric notor for reducing hybrid vehicle.In other words, unidirectional turbine clutch 60 is mixing Turbine 32 is separated with the output hub 64 of torque-converters 10 under some operating conditions of power car, for example, in sliding mode, start In machine braking mode and regeneration mode.
Torsional vibration damper 16 is axially received in shell 12, positioned at the first shell shell of turbine 32 and shell 12 201Between, as shown in Figure 1.Torsional vibration damper 16 includes substantially annular driving (or input) component 80, circumferentially that This multiple circumferential elastic damping component 82 being equally spaced and at least one, preferably multiple driving (or output) components 84.According to the first exemplary embodiment of Fig. 1, elastic damping component 82 is configured to spiral (or coil) spring, and main shaft is basic On be circumferentially orientated.Other elastic components be can choose to replace or supplement spring 82.Drive member 80 and driven member 84 connect Close the circumferentially opposed end of elastic damping component 82.Therefore, drive member 80 is flexibly coupled by elastic damping component 82 To driven member 84, as known in the art.Therefore, because the elasticity of the elastic damping component 82 of twisting vibration is absorbed, resistance The driven member 84 of Buddhist nun's device assembly 16 can be rotated relative to drive member 80.
According to the first exemplary embodiment, the drive member 80 of damper assembly 16 and the lock piston master of lock piston 52 Body 54 fixedly (that is, immovably) is linked together by rivet 81, as in Fig. 1 and Fig. 2 best seen from.In turn, Each driven member 84 is immovably connected at the radially distant end of the turbine case 33 of turbine 32 by device appropriate (that is, being fixedly connected to) arrives the annular turbine shell 33 of turbine 32, such as passes through welding at weld seam 85 or machanical fastener. In other words, lock piston 52 is elastically attached to turbine 32 by elastic damping component 82, in lock piston 52 and whirlpool Limited relative rotary motion is carried out between wheel 32.Further, since lock piston 52 can be along rotation axis X relative to output hub 64 axial movements, therefore lock piston 52 can be moved axially relative to the output link 84 of torque-vibration damper 16.
Lock-up clutch 18 is arranged for locking drive shaft and driven shaft.Lock-up clutch 18 usually rises in motor vehicles Start after dynamic and after drive shaft and the connection of driven shaft fluid power, to avoid loss in efficiency, especially by turbine 30 and leaf Loss in efficiency caused by sliding phenomenon between wheel 32.Lock piston 52 can be towards the 25 (locking of locking surface in shell 12 Engagement (or locking) position of clutch 18) and (separation of lock-up clutch 18 (or is beaten far from shell 12 locking surface 25 Open) position) it is axially displaced.In addition, lock piston 52 can far from torsional vibration damper 16 (lock-up clutch 18 engagement (or Locking) position) and it is axially displaced towards torsional vibration damper 16 (separation (or opening) position of lock-up clutch 18).Specifically Ground, the cylindrical lip 58 of lock piston main body 54 are installed to the cylinder-piston surface 69 of the annular piston flange 68 of output hub 64 On, so as to the cover housing 20 relative to output hub 64 and shell 121It centers, is rotatable and axially slidably shift.It is as follows What face was discussed in further detail, lock piston 52 is axially movable along rotation axis X relative to cover housing 20.Lock piston 52 Along the ring damper pressure chamber 23 exported in axially opposed sides of the axial movement of hub 64 by being positioned at lock piston 541、232 Control, as shown in Figure 1.
Lock piston 54 is selectively pressed against the locking surface 25 of shell 12, so that torque-converters 10 is locked in drive shaft Between driven shaft, and therefore control the sliding motion between turbine 32 and impeller 30.Specifically, it hydraulic is applied to when appropriate When lock piston 52, the locking surface 25 of lock piston 52 towards shell 12 simultaneously moves right (as shown in Figure 1) far from turbine 32, And friction facing 56 is clipped between the mating surface 55 of piston main body 54 and the locking surface 25 of shell 12.As a result, when lock When only clutch 18 is in the locked position, lock-up clutch 18 by torque-vibration damper 16, turbine 32 and unidirectional turbine from Clutch 60, which operationally connects shell 12, is connected to output hub 64.Therefore, when lock-up clutch 18 is in its latched position, Do not bypass turbine 32.
In operation, when lock-up clutch 18 is in separation (opening) position and when turbine 32 is rotated than output hub 64 When faster, engine torque is transmitted to output by unidirectional turbine clutch 60 from impeller 30 by the turbine 32 of fluid connector 14 Hub 64.When lock-up clutch 18 is in engagement (locking) position, engine torque passes through torque-vibration damper by shell 12 16, turbine 32 and unidirectional turbine clutch 60 are transmitted to output hub 64.However, when hybrid vehicle be in sliding mode, When engine braking modes or regeneration mode, that is, when exporting hub 64 can quickly rotate than turbine 32, unidirectional turbine clutch Device 60 separates turbine 32 from the output hub 64 of torque-converters 10, and torque is not transmitted to turbine 32 from output hub 64.
Method for assembling dynaflow torque converter 10 is as follows.It should be understood that the illustrative methods can be in conjunction with herein The other embodiments of description are practiced.The illustrative methods are not intended to assemble the exclusiveness side of turbine assembly as described herein Method.Although the method for assembling dynaflow torque converter 10 can be implemented by sequentially executing step as described below, It is it should be understood that this method may include being executed in different order these steps.
It is possible, firstly, to pre-assembly impeller 30, turbine 32, stator 34 and the torque-vibration damper with lock piston 52 16.Impeller 30 and turbine 32 are formed by steel billet punching press or by the injection molding of polymeric material.Stator 34 with aluminium by being cast It makes or injected polymeric material is made.Impeller 30, turbine 32 and 34 sub-component of stator fit together, to form tprque convertor 14。
First exemplary embodiment according to the present invention, turbine 32 is by formed below: annular turbine shell 33；One or more A (preferably three) coupling member 77A, from the radial inner end 33i of annular turbine shell 33 along towards cover housing 201Direction base Originally it extends axially outward；With one or more (preferably three) holding plates 77R, from the radial inner end of annular turbine shell 33 33i is approximately radial to extend internally, as best seen in Fig. 2 and 5-7.First exemplary embodiment according to the present invention has connection Connection member 77AWith holding plate 77RTurbine case 33 be one (or monomer) component, such as be made of single component, but can also be with It is the separation unit being permanently connected together.
Then unidirectional turbine clutch 60 is added.Turbine 32 is installed to unidirectional turbine clutch 60, so that turbine 32 Each coupling member 77AMatchingly engagement is formed in the cylindricality radial direction appearance of the main body 72 of the outer ring 62 of unidirectional turbine clutch 60 One in recess 63 in face 73, so as not to be rotationally coupled the outer ring 62 of turbine 32 and unidirectional turbine clutch 60, such as In Fig. 1-3 and 8 best seen from.Holding plate 77RBe arranged in the diameter of unidirectional turbine clutch 60 to the left near, with unidirectional turbine The directing plate 74 of the outer ring 62 of clutch 60 is axially opposing.
Then torque-vibration damper 16 is added.Before assembling torque-vibration damper 16, driven member 84 passes through suitable When device at the radially distant end of the turbine case 33 of turbine 32 immovably connection (that is, being fixedly connected to) arrive turbine 32 annular turbine shell 33, such as pass through welding at weld seam 85 or machanical fastener.Next, will by mode appropriate The lock piston main body 54 of lock piston 52 is fixed to the input link 80 of torque-vibration damper 16, such as by welding, gluing It connects or fastener (such as rivet 81).
Then input link 80 is elastically attached to by output link 84 by elastic damping component 82 to assemble torsion vibration Fluctuation dampers 16.Meanwhile the cylindrical lip 58 of piston main body 54 slides axially and is installed to output hub 64.Then, outside first shell Shell 201Immovably and it is sealingly secured to second shell shell 202, such as by being welded at 19, as shown in figure 1 most preferably It shows.
It can use above-described embodiment and realize various modifications, change and substitution, shown in including but not limited to Figure 10-22 Additional embodiment.For simplicity, in addition to the additional embodiment of explanation figure 10-22 it is required or useful other than, tie above It closes and is no longer further described below fixed reference feature that Fig. 1-9 is discussed, in Figure 10-22.By to the attached of part or part Icon note adds number 100 to indicate the part or part of modification.
In the dynaflow torque converter 110 of second exemplary embodiment shown in Figure 10-12, unidirectional turbine clutch 60 It is replaced by unidirectional turbine clutch 160.The dynaflow torque converter 110 of Figure 10-12 corresponds essentially to the fluid dynamic of Fig. 1-9 Torque-converters 10, therefore will be described in detail the unidirectional turbine clutch 160 of main difference below.
According in such as Figure 10-12 best seen from the second exemplary embodiment of the invention, unidirectional turbine clutch 160 matches Being set to prevents turbine 32 from reversely rotating.In other words, it is similar to unidirectional turbine clutch 60, unidirectional turbine clutch, 160 allow whirlpool Wheel 132 is only rotated along a circumferential direction.Unidirectional turbine clutch 160, as best shown in figure 11, comprising: with Rotation axis X coaxial outer ring 62；Inner ring 164, it is coaxial with outer ring 62 and be radially spaced with outer ring 62, to allow 62 He of outer ring Inner ring 164 is respectively relative to mutually rotating；With with multiple joint elements 66, the multiple joint element 66 is circumferentially disposed at In the annular space limited between outer ring 62 and inner ring 164.
It is also similar to unidirectional turbine clutch 60, the outer ring 62 of unidirectional turbine clutch 160 has annular radial outside track Surface 62R, and inner ring 164 has and radial outside track surface 62RDiametrically and annular radial inner orbit surface spaced apart 164R.As best seen in Figure 12, the radial inner orbit surface 164 of inner ring 164RIt is arranged radially at the radial outside track of outer ring 62 Surface 62RInside.Joint element 66 is configured to engage outside track surface 62 diametricallyRWith inner orbit surface 164R。
Unidirectional turbine clutch 160 also correspondingly includes the first and second bearing washers 94 of the sliding of the annular of low friction With 95.The first bearing washer 94 of low friction is axially disposed at the holding plate 77 of turbine 32RWith unidirectional turbine clutch 160 Between inner ring 164, to reduce rubbing between them when the outer ring 62 of turbine clutch 160 is rotated relative to its inner ring 164 It wipes.First bearing washer 94 is installed to the corresponding annular in the left axially outer side of the inner ring 164 of unidirectional turbine clutch 160 In recess portion, as in Figure 10-12 best seen from.Similarly, second bearing washer 95 is axially disposed at unidirectional turbine clutch Between the annular of the inner ring 164 of the directing plate 74 of 160 outer ring 62 and unidirectional turbine clutch 160, to reduce in unidirectional turbine The friction when outer ring 62 of clutch 160 is rotated relative to its inner ring 164 between them.The second bearing washer 95 of low friction It is installed in the respective annular recess portion in the right axially outer side of the inner ring 164 of unidirectional turbine clutch 160, as in Figure 10-12 Best seen from.
Each of first and second bearing washers 94 and 95 of low friction are made of durable low-friction material, such as Phenoplasts (or phenolic resin) or nylon.Also other suitable durable and low-friction plastic or other materials can be used.The One and second bearing washer 94 and 95 reduce unidirectional turbine clutch 160 component friction and wear.
In addition, the holding plate 77 of turbine 32RIt is configured to for joint element 66 being maintained between outer ring 62 and inner ring 164, and And prevent first bearing washer 94, inner ring 164 and the joint element 66 of unidirectional turbine clutch 160 relative to outer ring 62 along rotation Axial movement of the shaft axis X on direction from right to left, as shown in figure 11.Similarly, directing plate 74 is configured to joint portion Part 66 is maintained between outer ring 62 and inner ring 164, and prevents the second bearing washer 95 of unidirectional turbine clutch 160, inner ring 164 and axial movement of the joint element 66 relative to outer ring 62 along rotation axis X in the left to right direction, such as Figure 11 institute Show.
In the dynaflow torque converter 210 of the third exemplary embodiment shown in Figure 13-17, turbine 32 is by unidirectional turbine 232 replace, and unidirectional turbine clutch 60 is replaced by unidirectional turbine clutch 260.Dynaflow torque converter in Figure 13-17 210 correspond essentially to the dynaflow torque converter 10 of Fig. 1-9, therefore will be described in detail the turbine 232 of main difference below With unidirectional turbine clutch 260.Unidirectional turbine clutch 260 is configured to prevent turbine 232 from reversely rotating.In other words, unidirectionally Turbine clutch 260 allows turbine 232 to be only rotated along a circumferential direction.
Third exemplary embodiment according to the present invention, turbine 232 are formed with annular turbine shell 233, and from annular The holding plate 277 of the approximately radial general toroidal to extend internally of the radial inner end 233i of turbine case 233R, most such as Figure 14 and 15 It shows goodly.Third exemplary embodiment according to the present invention has holding plate 277RTurbine case 233 be one (or Monomer) component, such as be made of single component, but can be the separation unit being permanently connected together.
Unidirectional turbine clutch 260, as best seen in Figure 15, comprising: the outer ring 262 coaxial with rotation axis X；Inner ring 64, it is coaxial with outer ring 262 and be radially spaced with outer ring 262, to allow outer ring 262 and inner ring 64 to be respectively relative to revolve each other Turn；With multiple joint elements 66, the multiple joint element 66 is circumferentially disposed at the ring limited between outer ring 262 and inner ring 64 In shape space.Outer ring 262 has annular radially outer raceway surface 262R, and inner ring 64 has and radial outside track surface 262R Diametrically and annular radial inner orbit surface 64 spaced apartR.As best seen in Figure 15, the radial inner orbit table of inner ring 64 Face 64RIt is arranged radially at the radial outside track surface 262 of outer ring 262RInside.Joint element 66 is configured to engagement diametrically Outside track surface 262RWith inner orbit surface 64R。
Turbine 232 is non-rotatably attached to and (is fixed to) outer ring 262 of unidirectional turbine clutch 260.Specifically, such as In Figure 15,17A, 17B and 18 best seen from, the holding plate 277 of turbine 232RIt is immovably attached by mode appropriate The outer ring 262 that (that is, fixed) arrives unidirectional turbine clutch 260, is such as connect by welding, bonding or fastener, such as screw thread The threaded fastener 261 for closing the threaded hole 276 in the main body 272 of the outer ring 262 of unidirectional turbine clutch 260, as in Figure 16 most It is good to show.Annular retaining plate 277RIt is fixedly attached to the main body 272 of the inner ring 262 of unidirectional turbine clutch 260, and it is unidirectional The directing plate 274 of the outer ring 262 of turbine clutch 260 is axially opposing.
In addition, the holding plate 277R of turbine 232 is arranged between the first thrust bearing 421 and unidirectional turbine clutch 260, As in Figure 13 best seen from.Holding plate 277R is configured to for joint element 66 being maintained between outer ring 262 and inner ring 64, and Prevent unidirectional turbine clutch 260 joint element 66 and inner ring 64 relative to outer ring 262 along rotation axis X from right to left Direction on axial movement, as shown in figure 13.
In operation, when lock-up clutch 18 is in disengaged position (non-lockdown mode), engine torque is from impeller 30 Driven shaft is transmitted to by unidirectional turbine clutch 260 by fluid connector 214.When lock-up clutch 18 is in engagement (locking) (that is, (or being locked when lock piston 52 engaged by the effect of hydraulic pressure against the locking surface 25 of shell 12 when position It is fixed) when), engine torque is transmitted to driven shaft by torque-vibration damper 16 by shell 12.Specifically, engine torque from Shell 12 is transmitted to lock piston 52, and the input link 80 of torque-vibration damper 16 is then transmitted to from lock piston 52, is connect Be transmitted to the driven member 84 of torque-vibration damper 16 from input link 80 by elastic damping component 82, then from turbine Impeller 232 (being fixed to driven member 84) is transmitted to driven shaft by unidirectional turbine clutch 260.
Method for assembling fluid dynamic torque coupling arrangement 210 is as follows.It is possible, firstly, to pre-assembly impeller 30, whirlpool Wheel 232, stator 34 and the torque-vibration damper 16 with lock piston 52.Impeller 30 and turbine 232 by steel billet punching press or It is formed by the injection molding of polymeric material.Stator 34 of aluminum casting or injected polymeric material by being made.Impeller 30, turbine 232 and 34 sub-component of stator fit together, to form tprque convertor 214.
Third exemplary embodiment according to the present invention, turbine 232 are formed with annular turbine shell 233, and from annular The approximately radial annular retaining plate 277R to extend internally of the radial inner end 233i of turbine case 233, as Figure 15 is best shown. Third exemplary embodiment according to the present invention, the turbine case 233 with holding plate 277R are one (or monomer) component, example Such as it is made of single component but it is also possible to be the separation unit being permanently connected together.
Then unidirectional turbine clutch 260 is added.Turbine 232 is immovably attached to unidirectional turbine clutch 260, So that the holding plate 277 of turbine 232RThe outer ring of unidirectional turbine clutch 260 is immovably attached to by mode appropriate 262 main body 272, such as pass through welding, bonding or fastener, such as threaded fastener 261.More specifically, annular retaining plate 277RIt is fixedly attached to the outer ring 262 of unidirectional turbine clutch 260, the guidance with the outer ring 262 of unidirectional turbine clutch 260 Plate 274 is axially opposing.
Then, driven member 84 is not removable at the radially distant end of the turbine case 233 of turbine 232 by device appropriate (that is, fixed) is connected dynamicly and arrives the annular turbine shell 233 of turbine 232, such as passes through the welding or mechanical fasteners at weld seam 85 Part.Next, the lock piston main body 54 of lock piston 52 is fixed to torque-vibration damper 16 by mode appropriate Input link 80, such as pass through welding, bonding or fastener, such as rivet 81.
Then input link 80 is elastically attached to by output link 84 by elastic damping component 82 to assemble torsion vibration Fluctuation dampers 16.Meanwhile the cylindrical lip 58 of piston main body 54 is axially slidably installed to the cylinder-piston surface of output hub 64 69.Then, first shell shell 201Immovably and it is sealingly secured to second shell shell 202, such as by 19 Place's welding, as best shown in FIG. 1.
In the dynaflow torque converter 310 of the 4th exemplary embodiment shown in Figure 19-22, unidirectional turbine clutch 260 are replaced by unidirectional turbine clutch 360.The dynaflow torque converter 110 of Figure 19-22 corresponds essentially to the stream of Figure 13-18 Body power torque-converters 210, therefore will be described in detail more different unidirectional turbine clutchs 360 below.
According in such as Figure 19-22 best seen from the 4th exemplary embodiment of the invention, unidirectional turbine clutch 360 matches Being set to prevents turbine 232 from reversely rotating.In other words, it is similar to unidirectional turbine clutch 260, unidirectional turbine clutch 360 is permitted Perhaps turbine 232 is only rotated along a circumferential direction.Unidirectional turbine clutch 360, as best seen in Figure 22, packet It includes: the outer ring 262 coaxial with rotation axis X；Inner ring 364, it is coaxial with outer ring 262 and be radially spaced with outer ring 262, to allow Outer ring 262 and inner ring 364 are respectively relative to mutually rotating；With with multiple joint elements 66, the multiple joint element 66 weeks It is arranged in the annular space limited between outer ring 62 and inner ring 364 to ground.
It is also similar to unidirectional turbine clutch 260, the outer ring 262 of unidirectional turbine clutch 360 has annular radial outer rail Road surface 262R, and inner ring 364 has and radial outside track surface 262RDiametrically and annular radial inner orbit spaced apart Surface 364R.As best seen in Figure 22, the radial inner orbit surface 364 of inner ring 364RThe diameter for being arranged radially at outer ring 262 is outside Raceway surface 262RInside.Joint element 66 is configured to engage outside track surface 262 diametricallyRWith inner orbit surface 364R。
Unidirectional turbine clutch 360 also correspondingly includes the first and second bearing washers 94 of the sliding of the annular of low friction With 95.The first bearing washer 94 of low friction is axially disposed at the holding plate 277 of turbine 232RWith unidirectional turbine clutch 360 Inner ring 364 between, so as to when the outer ring 262 of turbine clutch 360 relative to its inner ring 364 rotate when reduce between them Friction.First bearing washer 94 is installed to the corresponding ring in the left axially outer side of the inner ring 364 of unidirectional turbine clutch 360 In shape recess portion, as in Figure 10-12 best seen from.Similarly, second bearing washer 95 is axially disposed at unidirectional turbine clutch Between the annular of the inner ring 364 of the directing plate 274 of the outer ring 262 of device 360 and unidirectional turbine clutch 360, to reduce unidirectional The friction when outer ring 262 of turbine clutch 360 is rotated relative to its inner ring 364 between them.The second bearing of low friction Washer 95 is installed in the correspondence annular recess in the right axially outer side of the inner ring 364 of unidirectional turbine clutch 360, such as Figure 22 In best seen from.
Each of first and second bearing washers 94 and 95 of low friction are made of durable low-friction material, such as Phenoplasts (or phenolic resin) or nylon.Also other suitable durable and low-friction plastic or other materials can be used.The One and second bearing washer 94 and 95 reduce unidirectional turbine clutch 360 component friction and wear.
In addition, the holding plate 277 of turbine 232RIt is configured to for joint element 66 being maintained between outer ring 262 and inner ring 364, And prevent first bearing washer 94, inner ring 364 and the joint element 66 of unidirectional turbine clutch 360 relative to 262 edge of outer ring Axial movement of the rotation axis X on direction from right to left, as shown in figure 21.Similarly, directing plate 274 is configured to connect Close component 66 be maintained between outer ring 262 and inner ring 364, and prevent unidirectional turbine clutch 360 second bearing washer 95, The axial movement of inner ring 364 and joint element 66 relative to outer ring 262 along rotation axis X in the left to right direction, such as Shown in Figure 21.
The aforementioned of exemplary embodiment of the present invention is presented for purposes of illustration according to the regulation of Patent Law to retouch It states.This is not intended to exhaustive or limits the invention to exact form disclosed.Select embodiments disclosed above It is in order to be best described by the principle of the present invention and its practical application, to enable those skilled in the art to be suitble to The present invention is most preferably utilized with various embodiments and various modifications in the expected specific mode used, as long as following described herein Principle.Therefore, it is intended to cover any modification, purposes or the modification of the invention for using its General Principle.This Outside, it is intended to the contents being away from each other with the disclosure known to covering in fields of the present invention or in customary practice.Cause This can be changed foregoing invention in the case where not departing from the intent and scope of the present invention.The scope of the present invention is also anticipated Figure is defined by the following claims.

Claims (20)

1. a kind of dynaflow torque converter, for drive shaft and driven shaft to be linked together, comprising: rotation axis can be surrounded The shell of rotation；It can be around the impeller that rotation axis rotates；It can be rotated around rotation axis and axial relatively with the impeller The turbine of setting, the turbine and the impeller co-axially align can be simultaneously rotatably driven by the impeller hydraulic power；Axis To the stator between the impeller and the turbine；The turbine is allowed only to be rotated in a circumferential direction Unidirectional turbine clutch；And torque-vibration damper；The unidirectional turbine clutch includes: to be non-rotatably connected to institute State the outer ring of turbine；The inner ring being radially arranged in the outer ring；And be positioned radially within the outer ring and the inner ring it Between multiple joint elements, the multiple joint element is configured as allowing the outer ring relative to the inner ring only in a week It is rotated on direction；The turbine is nonrotatably coupling to the outer ring of the unidirectional turbine clutch；Institute State turbine include turbine case and extended radially inwardly from the turbine case and with turbine case one at least one Holding plate, at least one described holding plate are located between the stator and turbine one-way clutch；The twisting vibration damping Device includes can be around the input link of rotation axis rotation, multiple elastic components circumferentially acted on, and pass through elastic component It is elastically attached to the output link of the input link；The output link of the torque-vibration damper is non-rotatably attached To the turbine.
2. dynaflow torque converter according to claim 1, wherein the outer ring of the unidirectional turbine clutch includes having The main body of radially-outer surface and the directing plate extended radially inwardly from the main body.
3. dynaflow torque converter according to claim 2, wherein the radial inner end engagement of the directing plate is described unidirectional The outside guiding surface of the diameter of the inner ring of turbine clutch.
4. dynaflow torque converter according to claim 2 or 3 further includes being axially disposed within the unidirectional turbine clutch The directing plate of outer ring and the inner ring of the unidirectional turbine clutch between low friction bearing washer, with reduce in the list Friction when being rotated to the outer ring of turbine clutch relative to its inner ring between them.
5. the dynaflow torque converter according to any one of claim 2 to 5 further includes being axially disposed within the turbine The bearing washer of low friction between at least one described holding plate and the inner ring of the unidirectional turbine clutch, to reduce in institute State friction between them when turbine is rotated relative to the inner ring of the unidirectional turbine clutch.
6. the dynaflow torque converter according to any one of claim 2 to 5, wherein the turbine further includes at least one A coupling member, at least one described coupling member is from the turbine case along big towards the direction of the unidirectional turbine clutch Cause extends axially outward, and integrated with the turbine case and at least one described holding plate；And wherein, the turbine At least one described coupling member is nonrotatably coupling to the outer ring of the unidirectional turbine clutch.
7. dynaflow torque converter according to claim 6, wherein at least one described coupling member of the turbine is not It is movably attached to the radially-outer surface of the main body of the outer ring of the unidirectional turbine clutch.
8. dynaflow torque converter according to claim 6, wherein the main body packet of the outer ring of the unidirectional turbine clutch Include at least one recess complementary at least one coupling member described in the turbine；And wherein, at least one described connection Connection member matchingly engages at least one described recess, so as not to be rotationally coupled the turbine and the unidirectional turbine clutch The outer ring of device.
9. the dynaflow torque converter according to any one of claim 2 to 5, wherein described at least the one of the turbine A holding plate is nonrotatably coupling to the main body of the outer ring of the unidirectional turbine clutch.
10. dynaflow torque converter according to claim 1, wherein the turbine includes and the turbine case is integrated General toroidal holding plate, and wherein, annular retaining plate is immovably attached to the outer of the unidirectional turbine clutch Ring.
11. dynaflow torque converter according to claim 10 further includes being axially disposed within the unidirectional turbine clutch Inner ring and holding plate between low friction bearing washer, with reduce in the turbine relative to the unidirectional turbine clutch Inner ring rotation when friction between them.
12. dynaflow torque converter according to any one of the preceding claims further includes lock piston, the locking is lived Plug can move axially to the shell and move axially from the shell, selectively to make the locking in lockdown mode Piston is frictionally engaged against the shell.
13. dynaflow torque converter according to claim 12, wherein the lock piston is non-rotatably attached to institute It states input link and the output link relative to the torque-vibration damper can move axially
14. dynaflow torque converter according to claim 12 or 13, wherein the shell has locking surface, wherein The lock piston has the engagement surface for the locking surface for being axially facing the shell, and wherein, the lock piston is also Annular friction liner including being fixedly attached to the engagement surface of the lock piston.
15. dynaflow torque converter according to any one of the preceding claims further includes unidirectional clutch of stator, described Unidirectional clutch of stator is installed to the stator and only allows rotary motion of the stator only in a circumferential direction.
16. dynaflow torque converter according to claim 1, wherein the inner ring limits the output hub of the torque-converters.
17. a kind of method for assembling dynaflow torque converter, method includes the following steps: providing can be around rotation axis The first shell shell and second shell shell of the shell of rotation；Pre-assembled torque-converters, the pre-assembled torque-converters are provided It include: impeller, the turbine and stator being axially oppositely disposed with impeller；Turbine includes turbine case and from the turbine case It extends radially inwardly and at least one holding plate with the turbine case one；There is provided allows the turbine only in a circumferential direction The unidirectional turbine clutch being rotated on direction, the unidirectional turbine clutch includes: outer ring；It is radially arranged in outer ring Interior inner ring；And the multiple joint elements being radially positioned between outer ring and inner ring, the multiple joint element are configured to permit Perhaps outer ring is only rotated in a circumferential direction relative to inner ring；Coaxially, no by the turbine and rotation axis It is rotatably connected to the outer ring of the unidirectional turbine clutch, so that at least one described holding plate setting of the turbine exists Between the stator and turbine one-way clutch；Torque-vibration damper is provided, the torque-vibration damper includes that can enclose The input link rotated around rotation axis, multiple elastic components circumferentially acted on, and be elastically attached to by elastic component The output link of the input link；The output link of the torque-vibration damper is non-rotatably attached to the whirlpool Wheel；And the input link of the torque-vibration damper is elastically mounted to by institute by the elastic component circumferentially acted on State the output link of torque-vibration damper.
18. according to the method for claim 17, further comprising the steps of: offer lock piston；And not by the lock piston It is rotatably attached to the input link of the torque-vibration damper.
19. according to the method for claim 18, wherein the input link of the torque-vibration damper passes through the circumferential direction The elastic component of effect is elastically mounted to the output link of the torque-vibration damper, enables the lock piston phase The inner ring of output link and the unidirectional turbine clutch for the torque-vibration damper moves axially.
20. according to the method for claim 17, wherein pre-assembled torque-converters includes turbine, and the turbine includes and institute State the substantially annular holding plate of turbine case one；And turbine is wherein non-rotatably connected to the unidirectional turbine The step of outer ring of clutch includes the outer ring that annular retaining plate is non-rotatably connected to the unidirectional turbine clutch Step.
CN201780078988.5A 2016-12-21 2017-12-21 Torque coupling arrangement and its manufacturing method with torque-vibration damper and unidirectional turbine clutch Pending CN110100118A (en)

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US15/387,050 US10281020B2 (en) 2016-12-21 2016-12-21 Torque-coupling device with torsional vibration damper and oneway turbine clutch, and method for making the same
US15/387,050 2016-12-21
PCT/KR2017/015282 WO2018117707A1 (en) 2016-12-21 2017-12-21 Torque-coupling device with torsional vibration damper and one-way turbine clutch, and method for making the same

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021078238A1 (en) * 2019-10-25 2021-04-29 法雷奥凯佩科液力变矩器(南京)有限公司 Hydraulic torque converter having torsional vibration damper and motor vehicle comprising same

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11125311B2 (en) 2019-02-14 2021-09-21 Schaeffler Technologies AG & Co. KG Torque converter and method of assembly
US10962095B2 (en) * 2019-03-26 2021-03-30 Schaeffler Technologies AG & Co. KG Torque converter assembly with disconnect clutch
US10808822B1 (en) * 2019-05-10 2020-10-20 Valeo Kapec Co., Ltd. Hydrokinetic torque-coupling device having lock-up clutch with dual piston assembly and selectable one-way clutch

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0723851U (en) * 1993-10-07 1995-05-02 株式会社大金製作所 Lockup device for torque converter
US6003647A (en) * 1997-08-14 1999-12-21 Exedy Corporation Torque converter with lock-up clutch having a flow-restraining elastic friction member
US6079529A (en) * 1998-03-23 2000-06-27 Mannesmann Sachs Ag Torque converter
JP2004122879A (en) * 2002-10-01 2004-04-22 Mazda Motor Corp Power train structure for vehicle
US20070137962A1 (en) * 2005-12-20 2007-06-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch attached to an outer rim of a torque converter and method for installing a clutch in a torque converter
US20070251789A1 (en) * 2006-05-01 2007-11-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with turbine one-way clutch
US20080277222A1 (en) * 2007-05-09 2008-11-13 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with cooling fluid flow arrangement and arrangement for torque transfer to a damper
JP2008309257A (en) * 2007-06-15 2008-12-25 Yutaka Giken Co Ltd Power transmission device for vehicle
US20130284554A1 (en) * 2010-11-24 2013-10-31 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
US20130306423A1 (en) * 2010-11-24 2013-11-21 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
CN103917806A (en) * 2011-09-29 2014-07-09 丰田自动车株式会社 Vehicular fluid power transmitting device
US20140251744A1 (en) * 2013-03-08 2014-09-11 Schaeffler Technologies AG & Co. KG One-way turbine wedge clutch
CN205036813U (en) * 2014-08-25 2016-02-17 Avl动力工程公司 Torque converter subassembly and manual gear shifting ware
US9297448B1 (en) * 2014-10-23 2016-03-29 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US20160102743A1 (en) * 2014-10-09 2016-04-14 Valeo Embrayages Hydrokinetic torque coupling device with turbine-piston lock-up clutch and bevel gearing
US20160160972A1 (en) * 2014-12-05 2016-06-09 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member
US20160160977A1 (en) * 2014-12-05 2016-06-09 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having core lockup clutch, and related methods

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1724983A (en) 1927-03-31 1929-08-20 Carl W Weiss Roller-clutch bearing
US3282129A (en) 1963-12-31 1966-11-01 Ford Motor Co Multiple speed ratio hydrokinetic power transmission mechanism
JPS613984B2 (en) 1974-08-19 1986-02-06 Toyota Motor Co Ltd
WO1985001785A1 (en) 1983-10-11 1985-04-25 Ford Motor Company Hydromechanical transmission with split torque and regenerative torque flow paths
US4703840A (en) 1984-05-29 1987-11-03 Eaton Corporation Torsion damping mechanism
US4608883A (en) 1984-07-16 1986-09-02 Eaton Corporation Torsion damping mechanism
US4889012A (en) 1987-09-04 1989-12-26 General Motors Corporation Damping assembly for a torque converter clutch
JPH0812865B2 (en) * 1989-06-06 1996-02-07 株式会社東芝 Bipolar transistor and manufacturing method thereof
DE10015701B4 (en) * 2000-03-29 2007-10-25 Zf Sachs Ag Hydrodynamic coupling device
JP3747438B2 (en) 2001-11-20 2006-02-22 株式会社エクセディ Torque transmission device
JP3570553B2 (en) 2001-11-20 2004-09-29 株式会社エクセディ Torque transmission device
ATE430975T1 (en) * 2006-07-10 2009-05-15 Harman Becker Automotive Sys REDUCING BACKGROUND NOISE IN HANDS-FREE SYSTEMS
US7980992B2 (en) * 2006-12-11 2011-07-19 Schaeffler Technologies Gmbh & Co. Kg Multi function torque converter with turbine engine idle disconnect and method of controlling a multi function torque converter for engine idle disconnect
DE102009039996A1 (en) 2008-09-22 2010-03-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Two-piece pump hub for hybrid torque converter
KR101056850B1 (en) * 2008-12-29 2011-08-12 한국파워트레인 주식회사 Automotive Torque Converter
JP5508835B2 (en) 2009-12-22 2014-06-04 アイシン・エィ・ダブリュ工業株式会社 Drive device for hybrid vehicle
DE102010012965A1 (en) 2010-03-25 2011-09-29 Voith Patent Gmbh Powertrain for a motor vehicle
DE102011109667A1 (en) 2011-08-08 2013-02-14 Voith Patent Gmbh Transmission for a motor vehicle
US8545355B2 (en) 2011-10-11 2013-10-01 Ford Global Technologies, Llc Assembly method for hybrid electric transmission
JP5878893B2 (en) * 2013-07-11 2016-03-08 株式会社エクセディ Torque converter lockup device
US9322463B2 (en) * 2014-04-25 2016-04-26 Valeo Embrayages Hydrokinetic torque coupling device with centered lock-up clutch friction disc, and method for assembling the same
DE112015003280T5 (en) * 2014-07-16 2017-04-13 Schaeffler Technologies AG & Co. KG Torque converter clutch with reduced back pressure
JP6649950B2 (en) 2014-09-22 2020-02-19 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ Hybrid drive module with single damper
WO2016089591A1 (en) * 2014-12-02 2016-06-09 Schaeffler Technologies AG & Co. KG Normally engaged turbine clutch
US10288159B2 (en) 2016-05-13 2019-05-14 GM Global Technology Operations LLC Integrated clutch systems for torque converters of vehicle powertrains

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0723851U (en) * 1993-10-07 1995-05-02 株式会社大金製作所 Lockup device for torque converter
US6003647A (en) * 1997-08-14 1999-12-21 Exedy Corporation Torque converter with lock-up clutch having a flow-restraining elastic friction member
US6079529A (en) * 1998-03-23 2000-06-27 Mannesmann Sachs Ag Torque converter
JP2004122879A (en) * 2002-10-01 2004-04-22 Mazda Motor Corp Power train structure for vehicle
US20070137962A1 (en) * 2005-12-20 2007-06-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch attached to an outer rim of a torque converter and method for installing a clutch in a torque converter
US20070251789A1 (en) * 2006-05-01 2007-11-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with turbine one-way clutch
US20080277222A1 (en) * 2007-05-09 2008-11-13 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torque converter with cooling fluid flow arrangement and arrangement for torque transfer to a damper
JP2008309257A (en) * 2007-06-15 2008-12-25 Yutaka Giken Co Ltd Power transmission device for vehicle
US20130284554A1 (en) * 2010-11-24 2013-10-31 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
US20130306423A1 (en) * 2010-11-24 2013-11-21 Toyota Jidosha Kabushiki Kaisha Vehicle power transmission device
CN103917806A (en) * 2011-09-29 2014-07-09 丰田自动车株式会社 Vehicular fluid power transmitting device
US20140251744A1 (en) * 2013-03-08 2014-09-11 Schaeffler Technologies AG & Co. KG One-way turbine wedge clutch
CN205036813U (en) * 2014-08-25 2016-02-17 Avl动力工程公司 Torque converter subassembly and manual gear shifting ware
US20160102743A1 (en) * 2014-10-09 2016-04-14 Valeo Embrayages Hydrokinetic torque coupling device with turbine-piston lock-up clutch and bevel gearing
US9297448B1 (en) * 2014-10-23 2016-03-29 Valeo Embrayages Hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
US20160160972A1 (en) * 2014-12-05 2016-06-09 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member
US20160160977A1 (en) * 2014-12-05 2016-06-09 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having core lockup clutch, and related methods

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021078238A1 (en) * 2019-10-25 2021-04-29 法雷奥凯佩科液力变矩器(南京)有限公司 Hydraulic torque converter having torsional vibration damper and motor vehicle comprising same

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US10281020B2 (en) 2019-05-07
US20180172128A1 (en) 2018-06-21
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JP2020502458A (en) 2020-01-23
WO2018117707A1 (en) 2018-06-28

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Application publication date: 20190806